US4195536A - Planetary transmission - Google Patents

Planetary transmission Download PDF

Info

Publication number
US4195536A
US4195536A US05/748,572 US74857276A US4195536A US 4195536 A US4195536 A US 4195536A US 74857276 A US74857276 A US 74857276A US 4195536 A US4195536 A US 4195536A
Authority
US
United States
Prior art keywords
clutch
gear
brake
planetary
input
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/748,572
Other languages
English (en)
Inventor
Julius A. Clauss
John S. Ivey
Richard L. Smirl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Borg Warner Corp
Original Assignee
Borg Warner Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Borg Warner Corp filed Critical Borg Warner Corp
Priority to US05/748,572 priority Critical patent/US4195536A/en
Priority to CA290,029A priority patent/CA1070523A/en
Priority to GB45825/77A priority patent/GB1581293A/en
Priority to AU30409/77A priority patent/AU512735B2/en
Priority to IT29705/77A priority patent/IT1087315B/it
Priority to DE19772752079 priority patent/DE2752079A1/de
Priority to SE7713855A priority patent/SE437865B/xx
Priority to BR7708145A priority patent/BR7708145A/pt
Priority to JP14703777A priority patent/JPS5371752A/ja
Application granted granted Critical
Publication of US4195536A publication Critical patent/US4195536A/en
Assigned to BORG-WARNER CORPORATION, A DE CORP. reassignment BORG-WARNER CORPORATION, A DE CORP. ASSIGNMENT OF ASSIGNORS INTEREST. EFFECTIVE AS OF DEC. 31, 1987 Assignors: BORG-WARNER AUTOMOTIVE, INC., A DE CORP.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another

Definitions

  • the transmission disclosed herein provides a four forward speed transmission mechanism easily adapted for front or rear wheel drive mechanism where the transmission, engine and driving wheels are all at the same extremity of the vehicle.
  • the present solution includes a single input clutch or in the alternative an input torque converter connected by a single intermediate input shaft to two simple planetary gear sets and the input clutch of torque converter.
  • a pair or clutches for the planetary gear set are provided which are mounted immediately adjacent the gear set elements which they drivingly connect.
  • the brake mechanisms for the planetary gear set comprising two disc brake mechanisms of identical diameters, mounted adjacent one another in a location of the casing which minimizes space requirements and maximizes the torque capacity of the brake mechanism.
  • FIG. 1 is a cross sectional view through a transmission and axle combination embodying the principles of the present invention.
  • FIG. 2 is a view showing a modified form of transmission mechanism wherein the input clutch is replaced by a hydraulic torque converter.
  • the improved transmission mechanism of the present invention is illustrated and generally comprises an input section 12 including a friction clutch 14 and a planetary gear section 16. Between planetary gear section 16 and input section 12 is an output section 18 which includes a differential mechanism 20, adapted to drive axle shafts 22 and 24 connected to the driving wheels of the vehicle. Input section 12 is mounted in a casing 13 and joined with casing 13, is a casing 15 in which is mounted planetary section 16.
  • Input section 12 as shown in FIG. 1, includes a friction clutch or input means 14 for connecting shaft 26 driven by the engine to an input shaft 28 which interconnects clutch 14 and planetary section 16.
  • Clutch 14 includes a driving member 30 comprised of a sheet metal housing 32 and an annular reaction plate 34.
  • Housing 32 Mounted within housing 32 is an apply member including an apply plate 38 which is connected by an annular return member 42 with a Belleville return spring 44.
  • Apply plate 38 is engageable with a friction clutch disc 46 which has friction material on either side thereof, the disc thus being adapted to be forced by apply plate 38 against reaction plate 34 to clutch members 34 and 38 together for transferring drive from housing 30 driven by input shaft 26 through clutch disc 46 to input shaft 28.
  • Clutch disc 46 includes a damper spring assembly 50 on a diameter inward of the friction material on disc 46.
  • Damper assembly 50 may be of a known construction such as for example, shown in U.S. Pat. No. 3,380,566 of common assignee.
  • the damper assembly 50 serves to transfer drive to a central hub 52 which is splined to input shaft 28. Thus, when clutch 14 is engaged drive will be transferred from shaft 26 driven by the engine to input shaft 28.
  • Apply plate 38 is mounted on an annular piston member 54 which is axially moveable and apply plate 38 is thus moveable axially.
  • Piston 54 defines a fluid chamber 56 which is adapted to receive fluid pressure through appropriate fluid pressure channels when clutch 14 is to be engaged.
  • Housing 32 includes an inner cylindrical sealing member 58 which has an annular seal 60 affixed thereto adapted to have sealing engagement with an axially extending portion 62 on piston 54. Housing 32 is engaged by the inner diameter of Belleville spring 44.
  • the central hub 66 of housing 32 is drivingly connected to a pump assembly 70 provided within an inner casing wall 72.
  • Pump assembly 70 as illustrated is an internal-external gear type but may be of any known type of pump used in this environment. Housing 32 transfers drive from the engine to the pump 72 through hub 66, the hub 66 thus having a sliding driving engagement with an inner gear 74 of pump 70.
  • clutch 14 is engageable to provide drive to input shaft 28 to provide a driving input to planetary gear section 16.
  • Planetary gear section 16 includes a pair of simple planetary gear sets 80 and 82. In connection with the planetary gear sets 80 and 82 are four friction engageable disc devices as follows; a clutch 84, a clutch 86, a brake 88 and a brake 90. In addition a one-way clutch 220 is provided for gear sets 80 and 82.
  • Planetary gear set 80 includes a sun gear 92 attached to input shaft 28, a ring gear 94, and a planetary carrier member 96.
  • carrier member 96 Mounted on carrier member 96 are a series of planetary pinions 98 which mesh with ring gear 94 and sun gear 92 in a known manner.
  • a brake member 100 Attached to and a part of planetary carrier 96 is a brake member 100 which is formed of sheet metal and which has an axially extending portion 102 and a radially extending portion 104.
  • a sheet metal clutch member 106 Secured to the radially extending portion 104 is a sheet metal clutch member 106 which has a series of splines 108 formed therein. Clutch member 106 may be secured to radial flange 104 by electron beam welding or other known joining techniques.
  • annular clutch member 110 which has an axial portion 112 located radially outwardly of clutch member 106.
  • Axial portion 112 has a series of splines 114 formed on the inner diameter thereof similar to the construction of splines 108.
  • a series of interleaved clutch plates are provided with an engageable to connect external clutch member 112 with internal clutch member 106.
  • a first series of clutch plates 116 is connected to splines 114 on member 112 and interleaved therewith is a series of clutch plates 118 splined to clutch member 106.
  • Within housing 110 is a clutch cylinder 120 which has a piston 122 slidable therein. Piston 122 together with clutch housing 110 defines fluid pressure chamber 124.
  • Clutch housing 110 includes an internal axial hub member 130 which is splined to input shaft 28. Secured on hub 130 is a spring retainer 132. Springs 134 are provided serving to return piston 122 to the right when no fluid pressure exists in chamber 124 when clutch 86 is to be disengaged. Formed in axial portions 102 of brake member 100 is a series of external splines 140.
  • Planetary gear set 82 includes sun gear member 150, a ring gear member 152, and a planetary carrier member 154. Ring gear 152 is connected by an annular sheet metal drum 156 with planetary carrier 96 of planetary gear set 80.
  • Planetary carrier 154 includes a sheet metal clutch hub 158 on the left side thereof as viewed in FIG. 1, and a radial flange 160 is integral with an axially extending output shaft 162 which has splined thereon an output sprocket gear 164.
  • Hub 158 includes a series of external splines 170 formed in the sheet metal thereof.
  • cylindrical sheet metal drum 172 Secured to ring gear 94 of gear set 80 is cylindrical sheet metal drum 172 which has a spline or notched outwardly extending portion 174, which is adapted to drivingly engage an annular sheet metal reaction member 176.
  • Reaction member 176 includes a series of internal splines 178 formed in the sheet metal thereof, to which the portion 174 is splined and is thus adapted to transfer rotational torque between ring gear 94 and reaction member 176.
  • Clutch 84 is adapted to be engaged to connect hub 158 and reaction member 176, as will be explained.
  • Reaction member 176 includes an annular sheet metal cylinder 200 which has a piston 202 therein. Piston member 202 and cylinder 200 define a pressure chamber 204 therebetween.
  • a series of interleaved friction plates extend between splines 170 on flange 158 and splines 178 on reaction member 176.
  • a series of friction plates 206 is provided engaging splines 178 and interleaved therewith is a series of friction plates 208, engaging splines 170.
  • piston 202 When fluid pressure is received in chamber 204, piston 202 will move to the right to press plates 206 and 208 together to engage clutch 84 drivingly connect ring gear 94 and reaction member 176 with planetary carrier 154 through hub 158.
  • a retainer 210 Mounted within the internal diameter of the cylinder 200 is a retainer 210. Extending between retainer 210 and piston 202 is a series of coil springs 212 adapted to return piston 202 to the left as viewed in FIG. 1 when fluid pressure is released from chamber 204.
  • a one-way clutch mechanism 220 is provided which engages with reaction member 176 in a manner to be described.
  • Brake reaction member 176 has an axial flange 222 which defines an inner race 224.
  • a brake hub 226 is provided internal of one-way clutch 220 which defines an external race 228.
  • Mounted between races 228 and 224 are a series of sprags 230 adapted to provide a driving engagement between flange 222 and hub 226 in one direction of rotation only, as is well known in the prior art.
  • a brake flange 240 of sheet metal which has drum portion 242 having splines 244 thereon.
  • Hub 226 is also splined to a hollow shaft 245 which has a sun gear 150 thereon.
  • Shaft 245 is concentric with output shaft 162.
  • the transmission mechanism described herein includes a pair of friction brake units 88 and 90, which are now described.
  • Formed in and internally of casing member 15 is a series of internal splines 250 which are adapted to receive, in the case of brake 90, for example, a series of brake discs 252 which are externally splined to engage with splines 250.
  • Interleaved with brake discs 252 are brake discs 254 which engage splines 140 on brake member 100.
  • a brake cylinder 260 which has slidable therein a piston 262, which defines with cylinder 260 a fluid chamber 264. Also provided in cylinder 260 is a retainer 266.
  • a series of coil springs 268 extend between retainer 266 and piston 262. When fluid pressure is received in chamber 264 piston 262 will move to the left as viewed in FIG. 1, to bring into engagement brake discs 252 and 254 to engage brake 90 and thus, fix brake member 100 to casing 15 and hold member 100, planetary carrier 96, and ring gear 152 stationary.
  • Brake 88 is comprised of a series of brake discs 270 externally splined to engage splines 250 in casing 15. Interleaved with brake discs 270 are a series of brake discs 272 which are splined internally to engage splines 244 on flange 240. Defined within casing 15 is a brake cylinder 280 having slidable therein a piston 282. Piston 282 and cylinder 280 define a fluid chamber 284. Mounted in an internal diameter of cylinder 280 is a retainer 286. Extending between retainer 286 and piston 282 are a series of coil return springs 288 which are adapted to return piston member 282 to the left as viewed in FIG.
  • Output section 18 of the present transmission includes sprocket gear 164 driven by output shaft 162.
  • Engaged with sprocket gear 164 is a chain 300.
  • Chain 300 is also engaged with a sprocket 302 which forms a driving sprocket for the differential assembly 20 and thereby is operable to transfer drive to the driving axles shafts 22 and 24.
  • Differential mechanism 20 includes a beveled side gear member 304 connected through a universal joint assembly, 306 to drive shaft 24, and a beveled side gear 308 is connected through a universal joint assembly 310 to drive axle shaft 22.
  • Interconnecting the side gears 308 and 304 are a plurality of planetary pinions 312 which are rotatably mounted on a planetary pinion carrier member 314 which is fixed within a driving casing 316 of differential 20.
  • Ring gear 302 is bolted or secured to casing 316.
  • the unique transmission described above is functional to provide four forward driving ratios and reverse, having only four friction engageable elements, and two simple planetary gear sets.
  • the following table indicates which friction elements are engaged to establish each of the forward driving ratios and reverse.
  • the symbol "D” means disengaged and the symbol “E” means engaged.
  • the ratio values given are to be understood as typical of those obtained in a particular example of a transmission constructed in accordance with the present invention.
  • clutch 14 When second forward ratio is to be established clutch 14 remains engaged, brake 88 remained engaged, and clutch 84 is engaged.
  • clutch 84 When clutch 84 is engaged ring gear 94 is connected directly to carrier 154 and thus output shaft 162.
  • sun gear 92 driving and ring gear 94 directly connected to output shaft 162 by clutch 84, and sun gear 150 held stationary, carrier member 96 being connected to ring gear 152, compounded planetary drive of carrier 154 will be provided in the forward direction, which will be a forward driving ratio of 2.518, for example.
  • clutch 14 When third forward driving ratio is established clutch 14 remains engaged, clutch 84 is disengaged and clutch 86 is engaged. With clutch 86 engaged, planetary carrier 96 is drivingly connected to input shaft 28 and sun gear 92, locking up planetary gear set 80 such that it rotates as a unit with the input shaft. Thus, ring gear 152 will be driven in a forward direction by input shaft 28, with sun gear 150 held stationary by brake 88 and ring gear 152 rotating with input shaft 28, planetary carrier 154 and output shaft 162 in a forward direction at a reduced driving ratio of 1.535, for example.
  • clutch 14 When fourth driving ratio is to be established clutch 14 remains engaged, clutch 86 remains engaged, brake 88 is released and clutch 84 is engaged. With clutch 84 engaged and planetary gear set 80 being locked up by clutch 86, a direct drive to planetary carrier 154 and output shaft 162 from input shaft 28 is provided, thus providing a one-to-one locked up driving ratio.
  • clutch 14 When reverse driving ratio is to be engaged clutch 14 is engaged and brake 90 is engaged. With sun gear 92 driven in the forward direction by input shaft 28, and planetary carrier 96 being held stationary by brake 90, ring gear 94 will be driven in the reverse direction by sun gear 92. With ring gear 94 driving in the reverse direction by means of one-way clutch 220 (since the outer race 224 is rotating in a reverse direction) a connection between ring gear 94 and hub 226 and sun gear 150 is established. Due to ring gear 94 driving sun gear 150 in the reverse direction, and the fact that ring gear 152 of planetary set 82 is held stationary by brake 90, the output carrier 154 will drive output shaft 162 in the reverse direction at a reduced ratio which may, for example, be a 5.274 ratio.
  • the transmission mechanism 10 in a unique and novel manner provides four forward driving ratios and reverse from an extremely compact transmission arrangement. As will be apparent from the above table of ratios, functionally desirable ratio steps are provided. Secondly, since second ratio is established by taking over from one-way clutch 220 when clutch 84 is engaged it will be apparent to those of ordinary skill in the art that the smoothness of the ratio change from first to second ratio is enhanced.
  • starting of the vehicle or the shift to first ratio from neutral may be accomplished merely by bringing on or engaging brake 88.
  • the brake 88 is of a large diameter thus insuring proper torque capacity and can include a large number of plates to provide for minimum wear.
  • the converter assembly 400 would include a pump or impeller element 402 connected to shaft 26 to be driven by the engine and output turbine 404 is included which is connected on the inner diameter through splines to input shaft 28 to the transmission mechanism.
  • the torque converter assembly 400 would also include a stator or reaction member 406 in the fluid circuit between impeller 402 and 404.
  • the stator 406 engages a stationary hub 408 connected to a casing through a one-way device 410 as is well known in the prior art.
  • the engine could be directly connected to input shaft 28 through a damper assembly and the clutch 14 and torque converter 400 both not included in the drive connection.
  • the neutral is provided again by having none of the elements within the transmission mechanism 16 engaged and when first ratio is to be established brake 88 would be gradually engaged to gradually provide the forward driving ratio to the vehicle driving wheels. In such case when the vehicle is stopped, the brake 88 would be disengaged.
  • the transmission as shown herein is in the form of a center output type transmission it will be apparent to those of ordinary skill in the art, that the transmission may be easily reconstructed to make it an "in line" unit for normal front engine-rear drive vehicles.
  • the input clutch 14 or torque converter 400 would be connected to the right end of input shaft 28 adjacent to clutch 86, and output shaft 162 would extend from the other end of the transmission to connect with the drive line to the rear wheels.
  • band type brakes could be substituted therefore if desired.
  • band brakes may be desirable in those environments wherein it is important to maintain a minimum dimension in the radial direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
US05/748,572 1976-12-08 1976-12-08 Planetary transmission Expired - Lifetime US4195536A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US05/748,572 US4195536A (en) 1976-12-08 1976-12-08 Planetary transmission
CA290,029A CA1070523A (en) 1976-12-08 1977-11-01 Planetary transmission
GB45825/77A GB1581293A (en) 1976-12-08 1977-11-03 Planetary transmission
AU30409/77A AU512735B2 (en) 1976-12-08 1977-11-07 Vehicle transmission
IT29705/77A IT1087315B (it) 1976-12-08 1977-11-15 Meccanismo di trasmissione ad ingranaggi staelliti
DE19772752079 DE2752079A1 (de) 1976-12-08 1977-11-22 Kraftfahrzeuggetriebe
SE7713855A SE437865B (sv) 1976-12-08 1977-12-06 Vexelmekanism for ett motordrivet fordon
BR7708145A BR7708145A (pt) 1976-12-08 1977-12-07 Mecanismo de transmissao
JP14703777A JPS5371752A (en) 1976-12-08 1977-12-07 Speed change mechanism

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US05/748,572 US4195536A (en) 1976-12-08 1976-12-08 Planetary transmission

Publications (1)

Publication Number Publication Date
US4195536A true US4195536A (en) 1980-04-01

Family

ID=25010016

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/748,572 Expired - Lifetime US4195536A (en) 1976-12-08 1976-12-08 Planetary transmission

Country Status (9)

Country Link
US (1) US4195536A (en)van)
JP (1) JPS5371752A (en)van)
AU (1) AU512735B2 (en)van)
BR (1) BR7708145A (en)van)
CA (1) CA1070523A (en)van)
DE (1) DE2752079A1 (en)van)
GB (1) GB1581293A (en)van)
IT (1) IT1087315B (en)van)
SE (1) SE437865B (en)van)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4242924A (en) * 1978-09-21 1981-01-06 Borg-Warner Corporation Transmission mechanism
JPS5939349U (ja) * 1982-09-06 1984-03-13 三菱自動車工業株式会社 自動変速機のクラツチ制御装置

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2395459A (en) * 1943-07-08 1946-02-26 Borg Warner Automatic transmission
US2593568A (en) * 1946-03-02 1952-04-22 Borg Warner Transmission
US2821867A (en) * 1952-03-13 1958-02-04 Borg Warner Two path power flow turbine transmission
US3473415A (en) * 1968-04-11 1969-10-21 Ford Motor Co Multiple ratio power transmission mechanism with two simple planetary gear units
US3541886A (en) * 1969-04-14 1970-11-24 Ford Motor Co Two-speed transmission with two simple planetary gear units
US3614902A (en) * 1970-06-13 1971-10-26 Fiat Spa Planetary transmission
US3800626A (en) * 1973-01-26 1974-04-02 Gen Motors Corp Transversely mounted engine driven transmission
US3802294A (en) * 1972-09-28 1974-04-09 Borg Warner Automotive transmission
US3853023A (en) * 1969-04-30 1974-12-10 Nissan Motor Gear train arrangements
US3859872A (en) * 1969-08-25 1975-01-14 Borg Warner Automotive transmission
US3977272A (en) * 1975-05-05 1976-08-31 Borg-Warner Corporation Transmission mechanism
US3986413A (en) * 1975-07-03 1976-10-19 Ford Motor Company Four-speed automatic coupling transmission

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2395459A (en) * 1943-07-08 1946-02-26 Borg Warner Automatic transmission
US2593568A (en) * 1946-03-02 1952-04-22 Borg Warner Transmission
US2821867A (en) * 1952-03-13 1958-02-04 Borg Warner Two path power flow turbine transmission
US3473415A (en) * 1968-04-11 1969-10-21 Ford Motor Co Multiple ratio power transmission mechanism with two simple planetary gear units
US3541886A (en) * 1969-04-14 1970-11-24 Ford Motor Co Two-speed transmission with two simple planetary gear units
US3853023A (en) * 1969-04-30 1974-12-10 Nissan Motor Gear train arrangements
US3859872A (en) * 1969-08-25 1975-01-14 Borg Warner Automotive transmission
US3614902A (en) * 1970-06-13 1971-10-26 Fiat Spa Planetary transmission
US3802294A (en) * 1972-09-28 1974-04-09 Borg Warner Automotive transmission
US3800626A (en) * 1973-01-26 1974-04-02 Gen Motors Corp Transversely mounted engine driven transmission
US3977272A (en) * 1975-05-05 1976-08-31 Borg-Warner Corporation Transmission mechanism
US3986413A (en) * 1975-07-03 1976-10-19 Ford Motor Company Four-speed automatic coupling transmission

Also Published As

Publication number Publication date
JPS5371752A (en) 1978-06-26
GB1581293A (en) 1980-12-10
IT1087315B (it) 1985-06-04
JPS6149533B2 (en)van) 1986-10-30
AU512735B2 (en) 1980-10-23
CA1070523A (en) 1980-01-29
BR7708145A (pt) 1978-07-25
AU3040977A (en) 1979-05-17
SE7713855L (sv) 1978-06-09
SE437865B (sv) 1985-03-18
DE2752079A1 (de) 1978-06-22

Similar Documents

Publication Publication Date Title
US3977272A (en) Transmission mechanism
US4509389A (en) Four speed ratio transaxle with overdrive
JP3414077B2 (ja) 車両用自動変速機
US3996817A (en) Transmission including dual input clutch assembly
EP0762014B1 (en) Automatic transmission
US3802294A (en) Automotive transmission
US3491621A (en) Four speed-ratio automotive vehicle driveline
US4570503A (en) Countershaft transmission
US6835158B2 (en) Automatic transmission
US4635495A (en) Multi-speed reversible power transmission
US4242924A (en) Transmission mechanism
US4455890A (en) Overdrive device for automatic transmissions
US4223569A (en) Transverse transmission with parallel, coplanar axis
US4438663A (en) Planetary transmission gearing and output shaft retention means
US4934216A (en) Four speed inline transmission overdrive
US5129871A (en) Nonsynchronous five-speed transaxle having bidirectional coupling
AU766974B2 (en) Power train for automatic transmissions
US4033436A (en) Transmission and torque converter with lock-up clutch
US6830531B1 (en) Control strategy for load sharing between a friction clutch and one-way clutch to effect low and reverse gear ratios in a transmission
US3564938A (en) Transmission and control
JPH0118922Y2 (en)van)
US3491617A (en) Hydrokinetic torque converter transmission mechanism with an overdrive gear ratio
US4346623A (en) Variable speed planetary transmission
JPS6025663B2 (ja) 車輛用自動変速機
US2862403A (en) Transmission

Legal Events

Date Code Title Description
AS Assignment

Owner name: BORG-WARNER CORPORATION, A DE CORP.

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST. EFFECTIVE AS OF DEC. 31, 1987;ASSIGNOR:BORG-WARNER AUTOMOTIVE, INC., A DE CORP.;REEL/FRAME:005287/0001

Effective date: 19881122